EP0719389B1 - Dispositif de commande, notamment pour embrayage de vehicule automobile - Google Patents

Dispositif de commande, notamment pour embrayage de vehicule automobile Download PDF

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Publication number
EP0719389B1
EP0719389B1 EP95923421A EP95923421A EP0719389B1 EP 0719389 B1 EP0719389 B1 EP 0719389B1 EP 95923421 A EP95923421 A EP 95923421A EP 95923421 A EP95923421 A EP 95923421A EP 0719389 B1 EP0719389 B1 EP 0719389B1
Authority
EP
European Patent Office
Prior art keywords
control device
plate
transmission
hydraulic actuator
electric motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP95923421A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0719389A1 (fr
Inventor
Frank Chazot
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo SE
Original Assignee
Valeo SE
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo SE filed Critical Valeo SE
Publication of EP0719389A1 publication Critical patent/EP0719389A1/fr
Application granted granted Critical
Publication of EP0719389B1 publication Critical patent/EP0719389B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D28/00—Electrically-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D29/00—Clutches and systems of clutches involving both fluid and magnetic actuation
    • F16D29/005—Clutches and systems of clutches involving both fluid and magnetic actuation with a fluid pressure piston driven by an electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
    • Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
    • Y10T74/18696—Reciprocating or oscillating to or from alternating rotary including screw and nut including means to selectively transmit power [e.g., clutch, etc.]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18888—Reciprocating to or from oscillating
    • Y10T74/18896—Snap action

Definitions

  • the invention relates generally to devices such as an electric motor, which by through a transmission, acts on the piston of a hydraulic cylinder forming an element of output for the assembly, elastic assistance means, which, in parallel vis-à-vis the electric motor, act on one of the organs constituting the transmission, and the mechanical means of compensation, which ensure a controlled modulation of the action elastic assistance means on the organ in question the transmission.
  • control devices find in particular their application for controlling the clutch of a vehicle automobile, as described for example in the documents FR-A-2,523,743, 2,564,920 and 2,541,793 (US-A-4,878,396, US-A-4,671,400).
  • the electric motor When controlling the release of such a clutch, the electric motor ensures, through the transmission and output element, positioning suitable for the release bearing, the output element acting for example accordingly on the range of declutching usually associated therewith, however, under control of mechanical compensation means, means assist elastics develop the necessary axial force to balance the opposing force due to the diaphragm of the clutch.
  • the mechanical means of compensation advantageously allow these elastic means to be adapted assistance with the specific characteristics of the diaphragm.
  • the invention relates more particularly to the case where the element outlet is a hydraulic cylinder, which advantageously allows to more easily catch up with effects due to wear inevitable friction linings of the friction disc of the clutch, and on the piston of which the electric motor acts through transmission. This is the case, by example, in documents FR-A-2 611 615 and 2 614 661.
  • the transmission has two organs, namely a worm, which is locked in rotation on the output shaft of the electric motor, and a toothed wheel, against which the worm intervenes tangentially, and to which is articulated, in the manner a connecting rod, a pusher acting on the piston of the jack hydraulic, however that together the means compensation mechanics result from the fact that the means assist elastics act at a point on this wheel angularly spaced apart from the point at which it is articulated push button in question.
  • the subject of the invention is a control device of the kind concerned advantageously likely to be reduced in size and also having other advantages.
  • This control device is characterized in that mechanical means of compensation comprise at least one train of rollers, which, rotatably mounted around a fixed axis orthogonal to the axis of the hydraulic cylinder, comprises, away from this fixed axis, at least two rollers, namely, a first roller established in contact with a first tray which, linked in movement to the organ concerned with the transmission, is axially movable between two positions, one at a distance, the other projection, and a second roller established in contact with a second plate, on which the elastic means bear assistance, and which, while being stalled in rotation on the first plate, is mounted axially movable relative to this one.
  • mechanical means of compensation comprise at least one train of rollers, which, rotatably mounted around a fixed axis orthogonal to the axis of the hydraulic cylinder, comprises, away from this fixed axis, at least two rollers, namely, a first roller established in contact with a first tray which, linked in movement to the organ concerned with the transmission, is axial
  • the control device thus formed can advantageously have a relatively compact size reduced, both axially and transversely. It is all the more so as its main constituents, namely the electric motor, the spring constituting in practice the elastic assistance means, and the hydraulic cylinder, can advantageously extend along the same axis.
  • the transmission occurring between the electric motor and the hydraulic cylinder piston has two bodies in relation to screw-nut one with respect to the other, which is also favorable to a reduction of overall dimensions, both axially and transversely.
  • control device is preferably formed, separately, on the one hand, a mechanical sub-assembly, which includes the motor electric, transmission, elastic assistance means and the mechanical means of compensation, and, on the other hand, a hydraulic sub-assembly, which is attached to the sub-assembly mechanical, and which comprises the hydraulic cylinder.
  • the cylinder body hydraulic is engaged axially in the sub-assembly mechanical, and, in addition to further reducing the axial size of the assembly, the body of this jack hydraulic can then advantageously form, if desired, a cylindrical guide bearing for the first plate of mechanical means of compensation, for the benefit of the conditions of these.
  • this first plate can also be provided by balusters duly provided for in this effect.
  • control device 10 comprises, overall, a motor electric 11, which, via a transmission 12, here mechanical, acts on the piston 13 of a hydraulic cylinder 14 forming an output element for the assembly, means assistance elastics 15, which, in parallel with respect to the electric motor 11, act, as explained subsequently, on one, 16, of the constituent bodies of the transmission 12, and mechanical compensation means 17, which ensure a controlled modulation of the action of the means assistance elastics 15 on this member 16.
  • control device 10 is formed, on the one hand, of a subset mechanical 10A, which includes the electric motor 11, the transmission 12, the elastic assistance means 15 and the mechanical compensation means 17, and on the other hand, a hydraulic sub-assembly 10B, which is attached to the sub-assembly mechanical 10A, here by two screws 18, and which comprises the hydraulic cylinder 14.
  • the mechanical sub-assembly 10A comprises a housing 20, of generally parallelepiped shape, the body of which 21 contains the transmission 12, the elastic assistance means 15 and the mechanical compensation means 17, and the cover of which 22, attached to the body 21 by screws 23, door externally, here in one piece, the motor housing electric there.
  • the hydraulic sub-assembly 10B intervenes on the side of the bottom 26 of the body 21, and therefore on the side of the housing 20 opposite the electric motor there.
  • the body 27 of the hydraulic cylinder 14 is, here, at least for part axially engaged in the mechanical sub-assembly 10A, at thanks to an opening 28 provided for this purpose in the bottom 26 of the body 21 of the housing 20, in the middle zone of this bottom 26.
  • Connection terminals 30 provide power electric motor electric it.
  • the shaft 31 of this electric motor 11 crosses, with interposition of a ball bearing 32, the cover 22 of the shoemaker 20, thanks to an opening 33 provided for this purpose in this cover 22, in the middle area thereof, and there extends along the axis Al of the hydraulic cylinder 14, that is to say along the direction of movement of the piston 13 thereof.
  • the transmission 12 comprises two bodies in relation of screw-nut with respect to each other, namely, on the one hand, a threaded rod 34, which is integral, both in rotation and in translation, of the shaft 31 of the electric motor 11, being for example in one piece with this tree 31, and, on the other hand, a threaded sleeve, which is in screw connection with the threaded rod 34, and which forms the member 16 on which act, as explained later, the elastic means assistance 15.
  • this threaded sleeve is here opened longitudinally by one or more slots 35, and, on at least part of its length, it is surrounded, externally, by a spring torsion 36 which is under stress.
  • the mechanical compensation means 17 comprise at least one roller train 37, which, mounted rotatable around an axis A2 fixed relative to the housing 20 and orthogonal to the axis A1 of the hydraulic cylinder 14, comprises, at the distance from this fixed axis A2, at least two rollers 38A, 38B, at namely, a first roller 38A established in contact with a first plate 39A, which, linked in movement to member 16 of the transmission 12, is axially movable between two positions, one moved back, Figures 1 and 4, the other advanced, Figure 6, and a second roller 38B established in contact with a second plate 39B, to which the elastic assistance means 15 relate, and which, while being locked in rotation on the first plate 39A, is mounted to move axially relative to the latter.
  • the fixed axis A2 is materialized by a shaft 49 mounted rotating in the body 21 of the housing 20.
  • the two plates 39A, 39B extend transversely by relative to the axis A1 of the hydraulic cylinder 14, coaxially with this one.
  • the first plate 39A extends on the side of the bottom 26 of the body 21 of the housing 20, and the second plate 39B on the side of the cover 22 of this housing 20.
  • the first plate 39A forms a flange at the end of a bowl 40, and the threaded sleeve forming the member 16 of the transmission 12 is backed by a flange 41 at the bottom 42 of this bowl 40, being fixed to this bottom 42 by screws 43.
  • the first plate 39A is thus integral, both in translation in rotation, of the member 16 of the transmission 12.
  • the bowl 40 has a slightly diameter greater than the outside diameter of the cylinder body 27 hydraulic 14, and, by its outlet, it is engaged on this one.
  • the body 27 of the hydraulic cylinder 14 can form a cylindrical guide bearing surface 45 for the first tray 39A.
  • this upright 46 has an internal bore axially 47 blind, to receive the threaded rod 34, for the benefit of axial compactness of the assembly.
  • the surfaces through which the upright 46 and the piston 13 of the hydraulic cylinder 14 axially bear one on the other are spherical, to compensate for a possible obliquity between the axis A3 of the electric motor 11 and that Al of the hydraulic cylinder 14.
  • the elastic assistance means 15 comprise a spring 48, of the coil spring type, coaxial with the jack hydraulic 14. This spring 48 extends around the sleeve threaded forming the member 16 of the transmission 12.
  • the mechanical compensation means 17 comprise two roller trains 37, which are arranged in positions diametrically opposed to each other on the one hand and on the other side of the axis A1 of the hydraulic cylinder 14, being symmetrical to each other with respect to this axis A1, and which both intervene between the two plates 39A, 39B.
  • the two rollers 38A, 38B of each of these trains of rollers 37 are rotatably mounted between two cheeks 50, around axes parallel to the corresponding fixed axis A2, and they intervene in the same diametral plane relative to the jack hydraulic 14.
  • the two rollers 38A, 38B are established in a triangle with the fixed axis A2.
  • each of the roller trains 37 comprises, obliquely, at away from its fixed axis A2, a ramp 51, which is interposed on the path of the first plate 39A between its positions moved back and advanced.
  • the first plate 39A bears on this ramp 51 by means of a spring 52, here a leaf spring, which is then under stress.
  • the spring 52 is attached by rivets 53 on the first plate 39A, on the side thereof opposite the second tray 39B.
  • the ramp 51 of each of the roller trains 37 is formed by the edge of the cheeks 50 thereof, and it belongs to a spout 56 formed by these cheeks 50 on the side of the fixed axis A2.
  • the bottom 26 of the body 21 of the housing 20 carries, annularly, on its internal surface, around the body 27 of the hydraulic cylinder 14, a ring 57, of elastic material, for form a limit stop for the first plate 39A when the latter is in the advanced position, Figure 6.
  • the piston 13 of the hydraulic cylinder 14 is subjected to a return spring 58 which, resting on the blind bottom of the body 27 of this hydraulic cylinder 14, constantly urges it towards the upright 46 of the mechanical sub-assembly 10A.
  • the body 27 of the hydraulic cylinder 14 is in connection with a pipe 61 capable of connecting it to the clutch to be controlled.
  • the hydraulic cylinder 14, and, more precisely, the body 27 thereof, is otherwise under the control of a solenoid valve 63, which, when energized, i.e. when electrically powered, is closed.
  • rollers 37 are hooked by their beak 56 on the first plate 39A of the mechanical compensation means 17, and their roller 38B is radially level with their fixed axis A2.
  • R B be the radius of the assembly on which this roller 38B is then located with respect to the axis A1 of the hydraulic cylinder 14.
  • the roller 38A of the roller trains 37 is located jointly on a radius R A less than the preceding radius R B.
  • the spring 48 constituting the elastic assistance means 15 is buttressed by the threaded sleeve constituting the member 16 of the transmission 12, this threaded sleeve being duly positioned by the threaded rod 34, and held in position axial by it, under the control of the electric motor 11.
  • the spring 48 is therefore in practice ineffective.
  • the spring 48 elastic assistance means 15 accompanies the member 16 of the transmission 12 in its axial displacement, by jointly subjecting it to an axial force assistance F 'which, in parallel with the axial force that jointly develops the electric motor 11 by via the transmission 12, allows movement concomitant axial of the piston 13 of the hydraulic cylinder 14, and, therefore, an increase in the pressure in the body 27 of this jack hydraulic 14.
  • this axial assistance force F ′ is in the following relation with respect to the axial force F actually developed by the spring 48, taking into account the multiplying coefficient due to the offset radial between the rollers 38B, 38A of the roller trains 37 of these mechanical compensation means 17:
  • F ' F x R AT R B
  • the radius R B decreases, while the radius R A remains substantially constant.
  • This representative curve thus looks like the curve characteristic of the diaphragm of the clutches, which allows the pressure in the body 27 of the hydraulic cylinder 14 to be at any time best suited to such a diaphragm.
  • This solenoid valve 63 also allows a catch-up wear, by a corresponding supply to the cylinder hydraulic 14.
  • the guidance of the first plate 39A is provided by balusters 65 duly provided for this purpose parallel to the axis A1 of the jack hydraulic 14 and integral with the body 21 of the housing 20.
  • the first plate 39A has arm 66 to cooperate with the roller trains 37 and it is provided a spacer sleeve 67 between the cheeks 50 thereof.
  • one of the roller trains 37 controls a potentiometer 68 externally attached to the body 21 of the housing 20, to allow position tracking.
  • the cursor not visible in the figure, of this potentiometer 68, is wedged by an arm 69 on an arm 70 itself wedged on the shaft 49 materializing the fixed axis A2, sufficiently extended to this effect, of the train of rollers 37 concerned.
  • the balusters 65 provide jointly a blocking in rotation of the first plate 39A.
  • a connection may be provided for this purpose. between the first plate 39A and the body 21 of the housing 20, such as, for example, a connection by tabs, or a post and mortise connection.
  • a splined connection can also be provided with the body 27 of the hydraulic cylinder 14.
  • the present invention is moreover not limited to embodiments described and shown, but encompasses any variant of execution and / or combination of their various elements, within the limits set by the claims.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Transmission Devices (AREA)
EP95923421A 1994-06-20 1995-06-20 Dispositif de commande, notamment pour embrayage de vehicule automobile Expired - Lifetime EP0719389B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9407518A FR2721264B1 (fr) 1994-06-20 1994-06-20 Dispositif de commande à vérin hydraulique piloté par un moteur électrique, notamment pour embrayage de véhicule automobile.
FR9407518 1994-06-20
PCT/FR1995/000821 WO1995035452A1 (fr) 1994-06-20 1995-06-20 Dispositif de commande, notamment pour embrayage de vehicule automobile

Publications (2)

Publication Number Publication Date
EP0719389A1 EP0719389A1 (fr) 1996-07-03
EP0719389B1 true EP0719389B1 (fr) 1998-03-25

Family

ID=9464395

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95923421A Expired - Lifetime EP0719389B1 (fr) 1994-06-20 1995-06-20 Dispositif de commande, notamment pour embrayage de vehicule automobile

Country Status (9)

Country Link
US (1) US5809830A (ko)
EP (1) EP0719389B1 (ko)
JP (1) JP3627150B2 (ko)
KR (1) KR100364180B1 (ko)
CN (1) CN1075173C (ko)
DE (1) DE69501874T2 (ko)
ES (1) ES2114746T3 (ko)
FR (1) FR2721264B1 (ko)
WO (1) WO1995035452A1 (ko)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007037095A1 (de) 2007-08-07 2009-02-12 Jopp Gmbh Ausrückvorrichtung, insbesondere für eine Fahrzeugkupplung

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Publication number Priority date Publication date Assignee Title
DE19504847B4 (de) * 1994-02-23 2006-04-27 Luk Gs Verwaltungs Kg Überwachungsverfahren für ein Drehmoment-Übertragungssystem eines Kraftfahrzeugs
DE19700935A1 (de) * 1996-01-31 1997-08-07 Luk Getriebe Systeme Gmbh Vorrichtung zur Betätigung eines Aggregates im Antriebsstrang eines Kraftfahrzeuges
JP3817297B2 (ja) * 1996-04-17 2006-09-06 ヴァレオユニシアトランスミッション株式会社 自動クラッチ
GB2351129B (en) * 1996-06-05 2001-02-21 Luk Getriebe Systeme Gmbh Operating device
GB2313885B (en) * 1996-06-05 2001-02-14 Luk Getriebe Systeme Gmbh Operating device
CN1059259C (zh) * 1996-12-29 2000-12-06 林纪功 自动离合器
DE19728828A1 (de) * 1997-07-05 1999-01-07 Bosch Gmbh Robert Stellantrieb für eine Fahrzeugkupplung
DE19728830A1 (de) * 1997-07-05 1999-01-07 Bosch Gmbh Robert Stellantrieb für eine Fahrzeugkupplung
JPH1163017A (ja) * 1997-08-15 1999-03-05 Aichi Mach Ind Co Ltd 自動クラッチ断続装置
JPH1182546A (ja) * 1997-09-12 1999-03-26 Aichi Mach Ind Co Ltd 摩擦クラッチの自動断続装置
FR2790806B1 (fr) * 1999-03-08 2001-04-27 Valeo Dispositif de commande pour moyen d'accouplement avec moderation d'effort variable
DE19943339A1 (de) 1999-09-10 2001-03-15 Rohs Voigt Patentverwertungsge Ausrückevorrichtung, insbesondere für eine Kupplung
FR2823544B1 (fr) 2001-04-11 2003-08-22 Renault Actionneur electrique a systeme de compensation compact, notamment pour commande d'embrayage ou de passage de vitesses sur une boite de vitesses robotisee
FR2831493B1 (fr) 2001-10-26 2004-01-02 Renault Dispositif de commande a distance, notamment pour la commande d'un embrayage d'entree de boite de vitesses robotisee
FR2862114B1 (fr) * 2003-11-12 2006-12-15 Valeo Embrayages Systeme de commande hydraulique d'un embrayage comportant des moyens d'assistance interposes entre l'emetteur et le recepteur du systeme.
FR2951033B1 (fr) 2009-10-06 2012-03-16 Valeo Embrayages Procede d'estimation en temps reel de la temperature du stator et du rotor d'une machine electrique tournante.
DE102011105501A1 (de) * 2010-06-29 2011-12-29 Schaeffler Technologies Gmbh & Co. Kg Hydrostataktor
EP2798233B1 (en) * 2011-12-27 2019-05-15 TVS Motor Company Limited Clutch actuator for an internal combustion engine
DE102014209808B4 (de) * 2013-11-25 2017-08-17 Magna powertrain gmbh & co kg Kupplung
FR3077351B1 (fr) 2018-01-31 2020-09-04 Valeo Embrayages Actionneur d'embrayage

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DE3309427A1 (de) * 1982-03-18 1983-10-06 Valeo Betaetigungsvorrichtung fuer eine kupplung, ein regelgetriebe, eine bremse, oder aehnliches
FR2541793B2 (fr) * 1983-02-25 1985-08-23 Valeo Commande pour un dispositif d'accouplement tel qu'embrayage, variateur de vitesse, frein ou analogue
FR2523723A1 (fr) * 1982-03-19 1983-09-23 Mitsubishi Atomic Power Ind Procede de detection d'une baisse de pression interne de gaz dans les produits du type recipient
DE3321578A1 (de) * 1983-06-15 1984-12-20 Sachs Systemtechnik Gmbh, 8720 Schweinfurt Steuerbarer antrieb fuer eine kraftfahrzeug-reibungskupplung
DE3504708A1 (de) * 1984-02-13 1985-08-14 Valeo, Paris Verschleissnachstellvorrichtung fuer die betaetigung einer kupplungsvorrichtung
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FR2610259B1 (fr) * 1987-02-03 1991-03-22 Valeo Dispositif de commande d'un moyen d'accouplement tel que par exemple un embrayage
DE3706849A1 (de) * 1987-03-03 1988-09-15 Sachs Systemtechnik Gmbh Stelleinrichtung, insbesondere fuer eine kraftfahrzeugreibungskupplung
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007037095A1 (de) 2007-08-07 2009-02-12 Jopp Gmbh Ausrückvorrichtung, insbesondere für eine Fahrzeugkupplung

Also Published As

Publication number Publication date
FR2721264B1 (fr) 1996-09-06
KR100364180B1 (ko) 2003-08-02
WO1995035452A1 (fr) 1995-12-28
DE69501874D1 (de) 1998-04-30
JPH09502251A (ja) 1997-03-04
DE69501874T2 (de) 1998-07-23
JP3627150B2 (ja) 2005-03-09
CN1075173C (zh) 2001-11-21
EP0719389A1 (fr) 1996-07-03
FR2721264A1 (fr) 1995-12-22
KR960704174A (ko) 1996-08-31
US5809830A (en) 1998-09-22
ES2114746T3 (es) 1998-06-01
CN1129969A (zh) 1996-08-28

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